US8506272B2 - Scroll compressor lubrication system - Google Patents

Scroll compressor lubrication system Download PDF

Info

Publication number
US8506272B2
US8506272B2 US12/891,157 US89115710A US8506272B2 US 8506272 B2 US8506272 B2 US 8506272B2 US 89115710 A US89115710 A US 89115710A US 8506272 B2 US8506272 B2 US 8506272B2
Authority
US
United States
Prior art keywords
cap
lubricant
radial
compressor
cage
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active, expires
Application number
US12/891,157
Other languages
English (en)
Other versions
US20110085925A1 (en
Inventor
Shuichong Fan
Linzhi Chao
Yu Fei
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Copeland Suzhou Co Ltd
Copeland Climate Technologies Suzhou Co Ltd
Original Assignee
Emerson Climate Technologies Suzhou Research and Development Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN201010273028.4A external-priority patent/CN102042230B/zh
Priority to US12/891,157 priority Critical patent/US8506272B2/en
Application filed by Emerson Climate Technologies Suzhou Research and Development Co Ltd filed Critical Emerson Climate Technologies Suzhou Research and Development Co Ltd
Priority to FR1003886A priority patent/FR2951231A1/fr
Assigned to EMERSON CLIMATE TECHNOLOGIES, INC. reassignment EMERSON CLIMATE TECHNOLOGIES, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: CHAO, LINZHI, FAN, SHUICHONG, FEI, YU
Priority to DE102010047724.9A priority patent/DE102010047724B4/de
Assigned to EMERSON CLIMATE TECHNOLOGIES (SUZHOU) RESEARCH & DEVELOPMENT CO., LTD. reassignment EMERSON CLIMATE TECHNOLOGIES (SUZHOU) RESEARCH & DEVELOPMENT CO., LTD. CORRECTIVE ASSIGNMENT TO CORRECT THE LEGAL NAME AND ADDRESS OF ASSIGNEE PREVIOUSLY RECORDED ON REEL 025103 FRAME 0902. ASSIGNOR(S) HEREBY CONFIRMS THE THE PARAGRAPH OF THE ORIGINAL ASSIGNMENT BEGINNING WITH "NOW, THEREFORE, FOR GOOD AND VALUABLE CONSIDERATION . . . ". Assignors: CHAO, LINZHI, FAN, SHUICHONG, FEI, YU
Publication of US20110085925A1 publication Critical patent/US20110085925A1/en
Publication of US8506272B2 publication Critical patent/US8506272B2/en
Application granted granted Critical
Assigned to EMERSON CLIMATE TECHNOLOGIES (SUZHOU) CO., LTD. reassignment EMERSON CLIMATE TECHNOLOGIES (SUZHOU) CO., LTD. MERGER AND CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: EMERSON CLIMATE TECHNOLOGIES (SUZHOU) CO., LTD., EMERSON CLIMATE TECHNOLOGIES (SUZHOU) RESEARCH & DEVELOPMENT CO., LTD.
Assigned to Copeland Climate Technologies (Suzhou) Co. Ltd. reassignment Copeland Climate Technologies (Suzhou) Co. Ltd. CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: EMESRON CLIMATE TECHNOLOGIES (SUZHOU) CO., LTD.
Active legal-status Critical Current
Adjusted expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/023—Lubricant distribution through a hollow driving shaft
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow

Definitions

  • the present disclosure relates to a compressor, and more particularly to a lubrication system for a compressor.
  • Cooling systems, refrigeration systems, heat-pump systems, and other climate-control systems include a fluid circuit having a condenser, an evaporator, an expansion device disposed between the condenser and evaporator, and a compressor circulating a working fluid (e.g., refrigerant) between the condenser and the evaporator.
  • the compressor may be one of any number of different compressors.
  • the compressor may be a scroll compressor or a reciprocating compressor that selectively circulates the working fluid among the various components of a cooling, refrigeration, or heat-pump system. Regardless of the particular type of compressor employed, consistent and reliable operation of the compressor is required to ensure that the cooling, refrigeration, or heat-pump system in which the compressor is installed is capable of consistently and reliably providing a cooling and/or heating effect on demand.
  • Compressors typically include a hermetic or semi-hermetic shell.
  • a partition disposed within the shell divides the shell into a suction-pressure zone and a discharge-pressure zone.
  • the working fluid is drawn into the suction-pressure zone and compressed by a compression mechanism and discharged therefrom into the discharge-pressure zone.
  • a lubricant sump may be disposed within the shell and stores a volume of lubricant, such as oil, for example.
  • the lubricant serves to lubricate the moving components of the compressor and can flow with the working fluid through the compression mechanism and into the discharge-pressure zone of the compressor.
  • the temperature of the lubricant and working fluid in the discharge-pressure zone is elevated relative to the lubricant and working fluid in the suction-pressure zone.
  • some or all of the lubricant is separated from the working fluid and returned to the lubricant sump.
  • the lubricant is subsequently recycled through the compressor and may interact with the working fluid being drawn in the suction-pressure zone of the compressor.
  • the elevated temperature of the lubricant raises the temperature of the working fluid in the suction-pressure zone, thereby increasing the superheat of the working fluid and reducing the volumetric efficiency of the compressor. Accordingly, it may be desirable to restrict an amount of lubricant flow through the compressor to minimize heating of the working fluid in the suction-pressure zone, while maintaining sufficient lubrication of the moving components of the compressor.
  • the present disclosure provides a lubricant metering system that may include a cap, a cap cage, and a shaft.
  • the cap may include an outer surface, a first recess, and a first radial bore extending between the first recess and the outer surface.
  • the cap cage may include a second recess receiving the cap and a lubricant inlet in communication with the first recess via the first radial bore.
  • the shaft may be received within the first recess and may include an axially extending bore and a second radial bore extending between an outer diameter of the shaft and the axially extending bore.
  • the shaft may be mounted for rotation relative to the cap to allow lubricant to flow into the axially extending bore via the first and second radial bores when the second radial bore is aligned with the first radial bore.
  • the present disclosure provides a lubricant metering system for a compressor that may include a lubricant source, a first cup-shaped member, a second cup-shaped member, and a shaft.
  • the first cup-shaped member may include a first recess in communication with the lubricant source.
  • the second cup-shaped member may be received in the first recess and may include a second recess and a radial bore in fluid communication with the lubricant source.
  • the shaft may be at least partially received in the second recess and may include an axially extending bore and a radially extending metering bore.
  • the radially extending metering bore may be in fluid communication with the axially extending bore and selective fluid communication with the radial bore of the second cup-shaped member.
  • the shaft may be mounted for rotation relative to the second cup-shaped member.
  • the second cup-shaped member may be mounted for transverse movement relative to the first recess of the first cup-shaped member to allow axial alignment of the second recess and the shaft relative to each other.
  • the present disclosure provides a compressor that may include a shell, a compression mechanism, a drive shaft, a motor, a lubricant sump, a cap, and a cap cage.
  • the compression mechanism is disposed within the shell.
  • the drive shaft drivingly engages the compression mechanism and may include an axially extending bore and a first radial aperture extending between an outer diameter of the drive shaft and the axially extending bore.
  • the motor drives the drive shaft.
  • the lubricant sump may be fluidly coupled with the compression mechanism to receive lubricant discharged from the compression mechanism.
  • the cap may include an outer surface, a first recess, and a second radial aperture extending between the first recess and the outer surface.
  • the cap cage may include a second recess receiving the cap and a lubricant inlet in communication with the first recess via the second radial aperture.
  • the drive shaft may be received within the first recess for rotation relative to the cap to allow lubricant to flow into the axially extending bore via the first and second radial apertures when the first radial aperture is aligned with the second radial aperture.
  • FIG. 1 is a perspective view of a compressor according to the principles of the present disclosure
  • FIG. 2 is a cross-sectional view of the compressor of FIG. 1 ;
  • FIG. 3 is an exploded perspective view of a lubricant metering system according to the principles of the present disclosure
  • FIG. 4 is a cross-sectional view of the metering system of FIG. 3 ;
  • FIG. 5 is a cross-sectional view of another metering system according to the principles of the present disclosure.
  • Example embodiments are provided so that this disclosure will be thorough, and will fully convey the scope to those who are skilled in the art. Numerous specific details are set forth such as examples of specific components, devices, and methods, to provide a thorough understanding of embodiments of the present disclosure. It will be apparent to those skilled in the art that specific details need not be employed, that example embodiments may be embodied in many different forms and that neither should be construed to limit the scope of the disclosure. In some example embodiments, well-known processes, well-known device structures, and well-known technologies are not described in detail.
  • Spatially relative terms such as “inner,” “outer,” “beneath,” “below,” “lower,” “above,” “upper” and the like, may be used herein for ease of description to describe one element or feature's relationship to another element(s) or feature(s) as illustrated in the figures. Spatially relative terms may be intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as “below” or “beneath” other elements or features would then be oriented “above” the other elements or features. Thus, the example term “below” can encompass both an orientation of above and below. The device may be otherwise oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
  • a compressor 10 is provided and includes a shell assembly 12 , a motor assembly 14 , a compression mechanism 16 , a lubricant metering system 18 , a discharge fitting 20 , and a suction gas inlet fitting 22 .
  • the compressor 10 circulates a working fluid (e.g., refrigerant) throughout a fluid circuit (not shown) of a refrigeration system, heat pump, or other climate-control system, for example. While the compressor 10 illustrated in the figures is a horizontal scroll compressor, the present teachings may be suitable for incorporation in many different types of vertical or horizontal scroll, rotary, and reciprocating compressors, for example, including hermetic machines, semi-hermetic machines, open-drive machines and non-hermetic machines.
  • the shell assembly 12 may house the motor assembly 14 , the compression mechanism 16 , and the lubricant metering system 18 .
  • the shell assembly 12 generally forms a compressor housing and may include a cylindrical shell 24 , a first end cap 26 , a second end cap 28 , a transversely extending partition 30 , and feet 32 .
  • the first end cap 26 and partition 30 may cooperate to form a discharge chamber 34 that functions as a discharge muffler for the compressor 10 .
  • a high-side lubricant sump 36 may be disposed within the discharge chamber 34 and stores a lubricant (e.g., oil) for distribution to the motor assembly 14 and compression mechanism 16 .
  • a lubricant e.g., oil
  • the lubricant sump 36 could be disposed outside of the shell assembly 12 .
  • the lubricant sump 36 may be a separate container fluidly coupled with a lubricant separator (not shown) disposed within the discharge chamber 34 .
  • the discharge fitting 20 is attached to the shell assembly 12 at a discharge opening 40 in the first end cap 26 .
  • a discharge valve assembly (not shown) may be located within the discharge fitting 20 and may prevent a reverse-flow condition to prevent high-pressure working fluid from entering the compressor 10 via the discharge fitting 20 .
  • the suction gas inlet fitting 22 is attached to the shell assembly 12 at a suction opening 38 in the shell 24 and is in fluid communication with a suction chamber 43 disposed within the shell assembly 12 .
  • the partition 30 separates the discharge chamber 34 from the suction chamber 43 and includes a discharge passage 44 providing communication between the compression mechanism 16 and the discharge chamber 34 .
  • the discharge-valve assembly could alternatively be located at or near the discharge passage 44 .
  • the motor assembly 14 includes a motor stator 46 , a rotor 48 , a drive shaft 50 , and windings that pass through the stator 46 .
  • the motor stator 46 may be press fit into the shell 24 to fix the stator 46 relative to the shell 24 .
  • the drive shaft 50 is rotatably driven by the rotor 48 , which may be press fit on the drive shaft 50 .
  • the drive shaft 50 may be rotatably supported at a first end by a main-bearing housing 54 and by a second bearing 56 at a second end.
  • the main-bearing housing 54 and the second bearing 56 are fixedly secured to the shell assembly 12 .
  • the drive shaft 50 may include an eccentric crank pin 58 having a crank pin flat 60 disposed thereon.
  • the drive shaft 50 may also include an axially extending bore 62 , radially extending metering bores 64 , and radially extending lubricant delivery bores 66 .
  • the metering bores 64 may include a diameter of about three (3) millimeters, for example. While the configuration shown in FIG.
  • the drive shaft 50 could include any number of metering bores 64 spaced apart from each other in any suitable arrangement.
  • the metering bores 64 may be in fluid communication with the axial bore 62 and may extend between the axial bore 62 and an outer diameter of the drive shaft 50 .
  • the axial bore 62 may extend from a first end 68 of the drive shaft 50 through a portion of the length of the drive shaft 50 and may be in communication with an eccentric bore 63 extending through a second end 70 of the drive shaft 50 .
  • One of the lubricant delivery bores 66 may extend radially between the axial bore 62 and an outer surface of the drive shaft 50 and may provide lubricant to the second bearing 56 .
  • Another of the lubricant delivery bores 66 may extend radially between the eccentric bore 63 and the outer surface of the drive shaft 50 and may provide lubricant to the main-bearing housing 54 .
  • the compression mechanism 16 may generally include an orbiting scroll 80 and a non-orbiting scroll 82 .
  • the orbiting scroll 80 includes an end plate 84 having a spiral vane or wrap 86 extending therefrom.
  • the orbiting scroll 80 may also include a cylindrical hub 88 that projects from the end plate 84 in a direction opposite the spiral wrap 86 and engages a drive bushing 90 .
  • the drive bushing 90 may include an inner bore in which the crank pin 58 is drivingly disposed. In one configuration, the crank pin flat 60 drivingly engages a flat surface in a portion of the inner bore of the drive bushing 90 to provide a radially compliant driving arrangement.
  • An Oldham coupling 98 may be positioned between orbiting scroll 80 and the main-bearing housing 54 and keyed to orbiting scroll 80 and non-orbiting scroll 82 .
  • the Oldham coupling 98 may engage the orbiting scroll 80 and the non-orbiting scroll 82 to prevent relative rotation therebetween while allowing the orbiting scroll 80 to orbit relative to the non-orbiting scroll 82 .
  • the lubricant metering system 18 may include a cap cage 100 , a cap 102 , a gasket 104 , a sealing plate 106 , and a lubricant conduit 108 fluidly coupling the lubricant metering system 18 and the lubricant sump 36 .
  • the lubricant metering system 18 may be secured to the second bearing 56 via a plurality of bolts 110 .
  • the cap 102 may be a generally cup-shaped member and may include a generally cylindrical body portion 128 , a protrusion 132 , and a radial bore 134 .
  • the body portion 128 may include an outer diameter 136 , an inner diameter 138 , an end wall 140 , and a rim 141 .
  • the inner diameter 138 and the end wall 140 may cooperate to define a generally cylindrical recess 142 .
  • the body portion 128 of the cap 102 may be received within the recess 118 of the cap cage 100 .
  • the protrusion 132 may extend from the outer diameter 136 of the cap 102 and may engage the slot 122 of the cap cage 100 to prevent relative rotation therebetween.
  • the recess 118 of the cap cage 100 and the body portion 128 of the cap 102 may be sized relative to each other to allow the cap 102 to move axially and radially relative to the recess 118 while the cap 102 is received within the recess 118 .
  • High-pressure lubricant from the lubricant conduit 108 may occupy a spaced between the cap 102 and the cap cage 100 , forming a high-pressure lubricant reservoir 143 .
  • the first end 68 of the drive shaft 50 may be received within the recess 142 and may be rotatable therein relative to the cap 102 .
  • the inner diameter 138 of the cap 102 and the outer diameter of the drive shaft 50 may be sized relative to each other to minimize the friction therebetween, while preventing or minimizing lubricant leakage therebetween.
  • the metering bores 64 are moved in and out of angular alignment with the radial bore 134 , thereby selectively allowing fluid communication between the axial bore 62 and the lubricant inlet 124 .
  • fluid communication between the axial bore 62 and the lubricant inlet 124 may be restricted or prohibited.
  • a second side of the sealing plate 106 may abut a first side of the gasket 104 .
  • the gasket 104 and/or the sealing plate 106 may be integrally formed with the second bearing 56 .
  • the second side of the gasket 104 may sealingly abut the cap cage 100 and the cap 102 .
  • the relatively high-pressure of the lubricant disposed within the high-pressure lubricant reservoir 143 may urge the rim 141 of the cap 102 into sealing engagement with the gasket 104 .
  • the gasket 104 and the sealing plate 106 cooperate to prevent fluid communication between the lubricant reservoir 143 and the recess 142 via any path other than through the radial bore 134 .
  • the sealed relationship between the cap cage 100 and the gasket 104 prevents lubricant from leaking therebetween into the suction chamber 43 .
  • the lubricant conduit 108 provides fluid communication between the lubricant sump 36 and the recess 118 of the cap cage 100 .
  • a fitting 154 may engage the lubricant inlet 124 and the lubricant conduit 108 and provide fluid communication therebetween.
  • the lubricant conduit 108 may be routed within the shell assembly 12 , as shown in FIG. 2 , or, alternatively, the lubricant conduit 108 could be routed externally from the shell assembly 12 .
  • Energizing the motor assembly 14 causes the drive shaft 50 to rotate, which in turn operates the compression mechanism 16 .
  • the compression mechanism 16 circulates the working fluid through the refrigeration system or heat-pump system.
  • relatively low-pressure working fluid is drawn into the suction chamber 43 via the suction gas inlet fitting 22 .
  • the low-pressure working fluid is drawn into the compression mechanism 16 and is compressed to a relatively high discharge-pressure.
  • the working fluid is then discharged from the compression mechanism 16 through the discharge passage 44 and into the discharge chamber 34 .
  • Lubricant in the compression mechanism 16 may be mixed in with the working fluid and discharged therewith into the discharge chamber 34 .
  • a lubricant separator 156 ( FIG. 2 ) disposed within the discharge chamber 34 filters or separates some or all of the lubricant from the working fluid. Once separated from the working fluid, the lubricant may fall from the lubricant separator, via gravity, into the lubricant sump 36 . In some configurations, the lubricant separator 156 may be disposed outside of the shell assembly 12 and provide lubricant to an external lubricant sump (not shown) disposed outside of the shell assembly 12 .
  • the lubricant inlet 124 of the cap cage 100 is in fluid communication with the suction chamber 43 via the radial bore 134 , the metering bores 64 , the axial bore 62 , the eccentric bore 63 , and the lubricant delivery bores 66 . Therefore, the pressure differential between the high-side lubricant sump 36 and the suction chamber 43 causes the high-pressure lubricant stored in the lubricant sump 36 to flow through the lubricant conduit 108 toward the cap cage 100 of the lubricant metering system 18 .
  • the lubricant flows through the fitting 154 and into the lubricant inlet 124 and into the high-pressure lubricant reservoir 143 disposed between the cap cage 100 and the cap 102 .
  • the relatively high-pressure lubricant disposed within the high-pressure lubricant reservoir 143 may urge the cap 102 in an axial direction such that the rim 141 of the cap 102 engages the gasket 104 .
  • the clearance between the outer diameter 136 of the of the cap 102 and the inner diameter of the recess 118 of the cap cage 100 allows the cap 102 to “float” or move in a radial direction relative to the cap cage 100 .
  • the cap 102 may be movable to “self-align” the axis of rotational symmetry of the recess 142 of the cap 102 with the rotational axis of the drive shaft 50 .
  • This self-aligning feature provides a more robust seal between the inner diameter 138 of the cap 102 and the outer diameter of the drive shaft 50 .
  • the axial bore 62 is in fluid communication with the lubricant inlet 124 via the radial bore 134 of the cap 102 and the metering bores 64 of the drive shaft 50 . Since the cap 102 is rotationally fixed relative to the cap cage 100 , and the drive shaft 50 is rotatable relative to the cap 102 , each of the metering bores 64 are only selectively communicating with the radial bore 134 . That is, the radial bore 134 may be in communication with one or more of the metering bores 64 when the one or more metering bores 64 are angularly aligned with the radial bore 134 . Accordingly, the lubricant flow rate into the axial bore 62 is dependent upon the number of metering bores 64 and the diameters of the metering bores 64 and the radial bore 134 .
  • the metering bores 64 are angularly spaced 180 degrees apart from each other. Therefore, while the compressor 10 is operating at a constant speed, lubricant flows into the axial bore 62 from the radial bore 134 twice, in equal increments, for every complete revolution of the drive shaft 50 .
  • the number of metering bores 64 , the spacing therebetween, and/or the diameters of the metering bores 64 and/or radial bore 134 may differ from the configuration described above to achieve a desired lubricant flow rate.
  • the metering bores 64 may be elongated in a direction parallel to the rotational axis of the drive shaft 50 to provide more tolerance with respect to the axial alignment of the metering bores 64 and the radial bore 134 .
  • a first portion of the lubricant may flow through the lubricant delivery bore 66 disposed therein to lubricate the second bearing 56 .
  • Centrifugal force causes a second portion of the lubricant to enter the eccentric bore 63 , through which the lubricant may flow along the length of the drive shaft 50 .
  • Lubricant may exit the eccentric bore 63 at the second end 70 of the drive shaft 50 and/or any remaining lubricant delivery bores 66 disposed in the eccentric bore 63 to be distributed to various components of the compressor 10 such as the rotor 48 , the main-bearing housing 54 , and/or compression mechanism 16 , for example.
  • lubricant may mix with the working fluid that is drawn into the compression mechanism 16 and is discharged therefrom at a relatively high pressure into the discharge chamber 34 and returned to the lubricant sump 36 . In this manner, the lubricant may be cycled between the lubricant sump 36 and the lubricant metering system 18 .
  • the structure and function of the lubricant metering system 218 may be generally similar to the structure and function of the lubricant metering system 18 described above, apart from the exceptions noted below.
  • the lubricant metering system 218 may include a cap cage 300 , a cap 302 , a wear plate 304 , a sealing member 306 , and the lubricant conduit 108 .
  • the lubricant metering system 218 may be bolted, press-fit and/or otherwise secured to the second bearing 56 .
  • the cap cage 300 may include a recess 318 , a slot 322 , and a lubricant inlet 324 .
  • the recess 318 may include an annular step 319 and an annular groove 321 disposed between the annular step 319 and an open end 323 of the recess 318 .
  • the lubricant inlet 324 may be in fluid communication with the lubricant conduit 108 to provide fluid communication between the lubricant sump 36 and the recess 318 , as described above.
  • the cap 302 may be received within the recess 318 and may include a protrusion 332 engaging the slot 322 , as described above.
  • the flange 152 of the second bearing 56 may be at least partially received in the recess 318 .
  • the wear plate 304 may be an annular disk-shaped member and may be received in the recess 318 and engage the annular step 319 .
  • the wear plate 304 may abut the cap 302 and the flange 152 of the second bearing 56 .
  • High-pressure lubricant between the cap cage 300 and the cap 302 biases the cap 302 against the wear plate 304 .
  • biasing the cap 302 against the wear plate 304 in this manner ensures axial alignment of the metering bores 64 in the drive shaft 50 with a radial bore 334 in the cap 302 and allows radial movement of the cap 302 relative to the cap cage 300 .

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US12/891,157 2009-10-12 2010-09-27 Scroll compressor lubrication system Active 2031-09-06 US8506272B2 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
US12/891,157 US8506272B2 (en) 2009-10-12 2010-09-27 Scroll compressor lubrication system
FR1003886A FR2951231A1 (fr) 2009-10-12 2010-09-30 Systeme de lubrification de compresseur a spirale
DE102010047724.9A DE102010047724B4 (de) 2009-10-12 2010-10-07 Schraubenkompressorschmiersystem

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
US25072309P 2009-10-12 2009-10-12
CN201010273028.4A CN102042230B (zh) 2009-10-12 2010-09-06 涡旋式压缩机润滑系统
CN201020517978.2 2010-09-06
CN201010273028.4 2010-09-06
CN 201020517978 CN201963553U (zh) 2009-10-12 2010-09-06 压缩机以及用于压缩机的润滑剂计量系统
US12/891,157 US8506272B2 (en) 2009-10-12 2010-09-27 Scroll compressor lubrication system

Publications (2)

Publication Number Publication Date
US20110085925A1 US20110085925A1 (en) 2011-04-14
US8506272B2 true US8506272B2 (en) 2013-08-13

Family

ID=43806825

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/891,157 Active 2031-09-06 US8506272B2 (en) 2009-10-12 2010-09-27 Scroll compressor lubrication system

Country Status (3)

Country Link
US (1) US8506272B2 (de)
DE (1) DE102010047724B4 (de)
FR (1) FR2951231A1 (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8944717B2 (en) * 2012-12-04 2015-02-03 Deere & Company Integrated pivot pin lubricator
US9598960B2 (en) 2013-07-31 2017-03-21 Trane International Inc. Double-ended scroll compressor lubrication of one orbiting scroll bearing via crankshaft oil gallery from another orbiting scroll bearing
US20210239118A1 (en) * 2020-02-04 2021-08-05 Aspen Compressor, Llc Horizontal rotary compressor with enhanced tiltability during operation and other performance metrics
US11994321B2 (en) 2019-01-03 2024-05-28 Aspen Compressor, Llc High performance compressors and vapor compression systems

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8449272B2 (en) * 2010-05-14 2013-05-28 Danfoss Scroll Technologies Llc Sealed compressor with easy to assemble oil pump
US8944790B2 (en) 2010-10-20 2015-02-03 Thermo King Corporation Compressor with cyclone and internal oil reservoir
US9341187B2 (en) 2013-08-30 2016-05-17 Emerson Climate Technologies, Inc. Compressor assembly with liquid sensor
US10125768B2 (en) * 2015-04-29 2018-11-13 Emerson Climate Technologies, Inc. Compressor having oil-level sensing system
CN205578273U (zh) * 2016-05-03 2016-09-14 艾默生环境优化技术(苏州)有限公司 泵油机构及具有该泵油机构的卧式压缩机
CN109386467B (zh) * 2017-08-03 2024-02-13 谷轮环境科技（苏州）有限公司 油分离装置和卧式压缩机
US11781548B2 (en) 2017-08-03 2023-10-10 Emerson Climate Technologies (Suzhou) Co., Ltd. Oil separation apparatus and horizontal compressor
EP3701151B1 (de) * 2017-10-24 2022-03-02 Carrier Corporation Schmiermittelzufuhrkanal für kompressorhintergrund

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4623306A (en) * 1984-03-05 1986-11-18 Mitsubishi Denki Kabushiki Kaisha Scroll compressor with bearing lubrication means
US5110268A (en) * 1989-12-04 1992-05-05 Hitachi, Ltd. Lubricant supply system of a scroll fluid machine
US5580233A (en) * 1994-09-16 1996-12-03 Hitachi, Ltd. Compressor with self-aligning rotational bearing
US6682322B2 (en) * 2001-10-31 2004-01-27 Hitachi, Ltd. Air-conditioner for use in an automobile
US6896496B2 (en) * 2002-09-23 2005-05-24 Tecumseh Products Company Compressor assembly having crankcase
US7566210B2 (en) * 2005-10-20 2009-07-28 Emerson Climate Technologies, Inc. Horizontal scroll compressor

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH062673A (ja) * 1992-06-18 1994-01-11 Daikin Ind Ltd 密閉横形スクロール流体機械
JPH1037872A (ja) * 1996-05-23 1998-02-13 Sanyo Electric Co Ltd 横型圧縮機
JP4881666B2 (ja) * 2006-07-07 2012-02-22 日立アプライアンス株式会社 横型スクロール圧縮機

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4623306A (en) * 1984-03-05 1986-11-18 Mitsubishi Denki Kabushiki Kaisha Scroll compressor with bearing lubrication means
US5110268A (en) * 1989-12-04 1992-05-05 Hitachi, Ltd. Lubricant supply system of a scroll fluid machine
US5580233A (en) * 1994-09-16 1996-12-03 Hitachi, Ltd. Compressor with self-aligning rotational bearing
US6682322B2 (en) * 2001-10-31 2004-01-27 Hitachi, Ltd. Air-conditioner for use in an automobile
US6896496B2 (en) * 2002-09-23 2005-05-24 Tecumseh Products Company Compressor assembly having crankcase
US7566210B2 (en) * 2005-10-20 2009-07-28 Emerson Climate Technologies, Inc. Horizontal scroll compressor

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8944717B2 (en) * 2012-12-04 2015-02-03 Deere & Company Integrated pivot pin lubricator
US9598960B2 (en) 2013-07-31 2017-03-21 Trane International Inc. Double-ended scroll compressor lubrication of one orbiting scroll bearing via crankshaft oil gallery from another orbiting scroll bearing
US10197059B2 (en) 2013-07-31 2019-02-05 Trane International Inc. Double-ended scroll compressor lubrication of one orbiting scroll bearing via crankshaft oil gallery from another orbiting scroll bearing
US11994321B2 (en) 2019-01-03 2024-05-28 Aspen Compressor, Llc High performance compressors and vapor compression systems
US20210239118A1 (en) * 2020-02-04 2021-08-05 Aspen Compressor, Llc Horizontal rotary compressor with enhanced tiltability during operation and other performance metrics
US11655820B2 (en) * 2020-02-04 2023-05-23 Aspen Compressor, Llc Horizontal rotary compressor with enhanced tiltability during operation
US20230313797A1 (en) * 2020-02-04 2023-10-05 Aspen Compressor, Llc Horizontal rotary compressor with enhanced tiltability during operation and other performance metrics

Also Published As

Publication number Publication date
DE102010047724A1 (de) 2011-05-05
FR2951231A1 (fr) 2011-04-15
DE102010047724B4 (de) 2019-09-19
US20110085925A1 (en) 2011-04-14

Similar Documents

Publication Publication Date Title
US8506272B2 (en) Scroll compressor lubrication system
US10415567B2 (en) Scroll compressor with axial flux motor
US10801495B2 (en) Oil flow through the bearings of a scroll compressor
CN108397382B (zh) 共旋转式压缩机
US10718330B2 (en) Co-rotating compressor with multiple compression mechanisms
US6619936B2 (en) Scroll compressor with vapor injection
US9239054B2 (en) Scroll compressor with oil-cooled motor
US20160025094A1 (en) Compressor motor with center stator
US8834139B2 (en) Lubrication of a scroll compressor
US20080152526A1 (en) Vapor injection system for a scroll compressor
US10036388B2 (en) Scroll compressor with oil management system
US10941772B2 (en) Suction line arrangement for multiple compressor system
WO2018145091A1 (en) Scroll compressor with axial flux motor
US12078173B2 (en) Compressor having lubrication system
US9695823B2 (en) Compressor with unloader counterweight assembly
US12104594B2 (en) Co-rotating compressor
US12092111B2 (en) Compressor with oil pump
CN111749899B (zh) 具有油配给构件的压缩机

Legal Events

Date Code Title Description
AS Assignment

Owner name: EMERSON CLIMATE TECHNOLOGIES, INC., OHIO

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:FAN, SHUICHONG;CHAO, LINZHI;FEI, YU;REEL/FRAME:025103/0902

Effective date: 20101007

AS Assignment

Owner name: EMERSON CLIMATE TECHNOLOGIES (SUZHOU) RESEARCH & D

Free format text: CORRECTIVE ASSIGNMENT TO CORRECT THE LEGAL NAME AND ADDRESS OF ASSIGNEE PREVIOUSLY RECORDED ON REEL 025103 FRAME 0902. ASSIGNOR(S) HEREBY CONFIRMS THE THE PARAGRAPH OF THE ORIGINAL ASSIGNMENT BEGINNING WITH "NOW, THEREFORE, FOR GOOD AND VALUABLE CONSIDERATION . . . ";ASSIGNORS:FAN, SHUICHONG;CHAO, LINZHI;FEI, YU;REEL/FRAME:025523/0502

Effective date: 20101007

STCF Information on status: patent grant

Free format text: PATENTED CASE

CC Certificate of correction
FPAY Fee payment

Year of fee payment: 4

MAFP Maintenance fee payment

Free format text: PAYMENT OF MAINTENANCE FEE, 8TH YEAR, LARGE ENTITY (ORIGINAL EVENT CODE: M1552); ENTITY STATUS OF PATENT OWNER: LARGE ENTITY

Year of fee payment: 8

AS Assignment

Owner name: EMERSON CLIMATE TECHNOLOGIES (SUZHOU) CO., LTD., CHINA

Free format text: MERGER AND CHANGE OF NAME;ASSIGNORS:EMERSON CLIMATE TECHNOLOGIES (SUZHOU) RESEARCH & DEVELOPMENT CO., LTD.;EMERSON CLIMATE TECHNOLOGIES (SUZHOU) CO., LTD.;REEL/FRAME:063580/0368

Effective date: 20110718

AS Assignment

Owner name: COPELAND CLIMATE TECHNOLOGIES (SUZHOU) CO. LTD., CHINA

Free format text: CHANGE OF NAME;ASSIGNOR:EMESRON CLIMATE TECHNOLOGIES (SUZHOU) CO., LTD.;REEL/FRAME:065196/0183

Effective date: 20230731